EP0583336B1 - Hydraulische gleitkupplung - Google Patents

Hydraulische gleitkupplung Download PDF

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Publication number
EP0583336B1
EP0583336B1 EP92910068A EP92910068A EP0583336B1 EP 0583336 B1 EP0583336 B1 EP 0583336B1 EP 92910068 A EP92910068 A EP 92910068A EP 92910068 A EP92910068 A EP 92910068A EP 0583336 B1 EP0583336 B1 EP 0583336B1
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EP
European Patent Office
Prior art keywords
track
coupling assembly
sinuate
assembly according
slider
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92910068A
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English (en)
French (fr)
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EP0583336A4 (en
EP0583336A1 (de
Inventor
Clifford Anthony Joachim
Stanislaw Spryszynski
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Invensys Australia Finance Pty Ltd
Original Assignee
BTR Engineering Australia Ltd
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Publication date
Application filed by BTR Engineering Australia Ltd filed Critical BTR Engineering Australia Ltd
Publication of EP0583336A1 publication Critical patent/EP0583336A1/de
Publication of EP0583336A4 publication Critical patent/EP0583336A4/en
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Publication of EP0583336B1 publication Critical patent/EP0583336B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
    • B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
    • B60K17/3505—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches with self-actuated means, e.g. by difference of speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D35/00—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion

Definitions

  • the present invention relates to variable torque-speed transmission couplings and in particular to a hydraulic slider coupling.
  • a viscous coupling is a torque transmitting element which functions by means of viscous friction whereby the torque-speed characteristic is dependent upon the rheological properties of the viscous filling medium which is usually a silicone based fluid.
  • viscous couplings have usually comprised sets of mutually interleaved parallel annular plates coaxially mounted for rotation within an hermetically sealed enclosure containing a viscous medium in contact with adjacent surfaces of the plates.
  • Alternate plates are connected with respective driving and driven elements such that an angular velocity differential across the coupling causes viscous shearing of the fluid in the annular clearance between adjacent plates to produce the desired speed-torque transmission characteristic.
  • Commonly used silicon based fluids in viscous couplings exhibit a degressive torque response with increasing rate of shear.
  • FR-A-974603 discloses a speed variator comprising (i) first and second members disposed for relative rotation, one of said first and second members including a circumferentially extending continuous and generally sinuate track, the other of said first and second members including a transverse track extending in a direction substantially normal to the general direction of the continuous and generally sinuate track, (ii) a slider located in an intersecting region of said sinuate and transverse tracks such that relative rotation of said first and second members causes said slider to oscillate axially within said transverse track while traversing said continuous and generally sinuate track, and (iii) a hydraulic medium within said sinuate track and said transverse track.
  • the object of the present invention is to provide a coupling assembly which can be used in a viscous slip drive coupling.
  • the invention consists in a coupling assembly comprising a first member and a second member disposed for relative rctational engagement, one of said first and said second members including a circumferentially extending continuous and generally sinuate track, the other of said first and said second members including a plurality of transverse tracks extending in a direction substantially normal to the general direction of the sinuate track, a corresponding plurality of sliders located respectively in intersecting regions of said sinuate and transverse tracks such that relative rotation of said first and said second members causes said sliders to oscillate axially within said transverse tracks while traversing said sinuate track, and a hydraulic fluid medium within said transverse tracks to provide a resistance to said oscillation of said sliders.
  • the first member is an inner hub including the sinuate track on an outer cylindrical surface thereof and the second member is a complementary outer hub supported for coaxial rotation with respect to the inner hub and defining said plurality of uniformly spaced axially extending transverse tracks in the form of grooves on an inner cylindrical surface thereof, the inner and outer hubs being mounted for relative coaxial rotation.
  • the sinuate track is periodic and in one form of the invention the track is sinusoidal.
  • the slider is in the form of a ball and the track and grooves are substantially semicircular in cross section.
  • each ball engages a prismatic slider for reciprocation within a complementary prismatic groove or bore.
  • the prismatic grooves are preferably rectangular in cross section.
  • a clearance is provided between each groove and associated slider through which the hydraulic fluid is throttled during reciprocation of the slider.
  • the slider may be in the form of a piston sealingly slidable within the groove and in this case the piston can include an orifice through which the hydraulic fluid is throttled to provide a predetermined resistive damping force.
  • each slider preferably comprises a cylindrical piston sealingly reciprocable within the respective groove and the hydraulic fluid is contained in a closed loop and throttled through a selectively adjustable control valve in response to reciprocation of the piston.
  • This form of the invention permits selective adjustment of the torque transfer characteristic for given differential coupling speeds and permits selection of a lock-up condition between the input and output hubs of the coupling by means of complete closure of the control valve.
  • the first member is an inner hub including a plurality of axially extending prismatic sliders angularly spaced around the periphery of the hub in complementary prismatic bores.
  • the second member includes two axially spaced apart outer hubs supported for coaxial rotation with respect to the inner hub and including complementary sinuate tracks for slidably engaging opposite axial ends of said sliders, the inner hub being mounted for relative rotation substantially within the outer hubs.
  • the prismatic sliders are generally rectangular in cross section and reciprocate in said bores during relative movement between said hubs.
  • the inner hub includes a plurality of axially extending fluid control slots around the periphery of said inner hub alternately spaced between said bores for decreasing the resistance to oscillation provided by the hydraulic fluid medium.
  • the invention consists in a torque proportioning differential mechanism having inherent torque bias, said differential mechanism including a carrier adapted to be rotatably driven about a longitudinal axis, a pair of coaxial parallel side gears supported for rotation about an axis fixed with respect to the carrier, at least one pinion rotatably mounted to said carrier and in meshing engagement with said side gears, and a coupling assembly substantially as herein described disposed effectively between said side gears or between one of said side gears and said carrier such that a difference in angular velocity between said side gears causes a corresponding difference in angular velocity across the coupling, thereby creating drag which enables unequal torque to be supported at each side gear.
  • a hydraulic ball coupling assembly 1 comprises an inner hub 2 and an outer hub 3 disposed for relative coaxial rotational engagement.
  • the inner hub 2 includes a continuous sinuate recessed track 4 extending circumferentially around the cylindrical outer surface 5.
  • the outer hub 3 includes a plurality of uniformly spaced axially extending grooves 6 on the inner cylindrical surface 7. The grooves 6 extend in a direction substantially normal to the general effective direction of the sinuate track 4.
  • a slider 10 is reciprocably disposed within each groove 6 and located in the intersecting region 11 of the sinuate track 4 and the respective groove such that relative rotation of the inner and outer hubs causes each slider 10 to oscillate axially within its respective groove 6 while traversing the track 4.
  • the grooves 6 and track 4 contain a hydraulic fluid of suitable viscosity to provide fluid resistance to the oscillation of the sliders and thereby permit transmission of torque between the driving and driven hubs.
  • the coupling preferably incorporates suitable sealing means intermediate the inner and outer hubs to contain the hydraulic fluid within the grooves and track.
  • suitable sealing means may not be required.
  • the inner and outer hubs are drivingly connected with respective input and output rotary drive shafts. Any difference in angular velocity between the driving and driven hubs causes the sliders 10 to traverse the sinuate track 4 which causes a corresponding reciprocating movement of the sliders within their respective grooves 6. This reciprocating movement is resisted by the hydraulic fluid medium to enable torque to be transmitted between the hubs.
  • the track 4 is preferably sinusoidal to provide smooth transmission of torque.
  • any suitable form of sinuate track could be used such as that illustrated in figure 3 which shows a modified sinusoidal form having dwell regions 12 at the positions of maximum amplitude.
  • each slider 10 is in the form of a steel ball 13 and the track 4 and grooves 6 are semi-oval shaped in cross section to contain the balls within the intersecting regions 11 of the track and grooves.
  • a peripheral clearance is provided through which the hydraulic fluid is throttled during reciprocation of the slider.
  • the reciprocating movement of the balls 13 causes viscous shearing of the fluid medium within the grooves to produce frictional drag which resists movement of the balls and thereby enables torque to be transferred between the driving and driven hubs.
  • a high viscosity fluid such as a silicon based liquid or grease is preferred to provide the requisite resistance to motion.
  • the slider 10 comprises a ball 13 in driving engagement with a rectangular prismatic sliding block 14 adapted for reciprocation within a complementary prismatic groove.
  • the longitudinally extending edges 15 of the sliding block 14 are chamfered to define clearance passages through which the hydraulic fluid is throttled as the ball 13 traverses the sinusoidal track.
  • the ball 13 engages a piston sealingly slidable within a complementary groove or bore and the piston includes an orifice through which the hydraulic fluid is throttled to provide a predetermined resistive damping force.
  • this form of the invention incorporating the orifice provides a more controlled flow and therefore more consistent torque transfer characteristics.
  • this form of the invention permits discrete adjustment of the torque-speed characteristic of the coupling by the substitution of different sized orifices thereby enabling the coupling performance characteristics to be tailored to suit particular applications.
  • Figures 10 to 12 show a further form of the invention wherein the ball 13 drivingly engages a cylindrical piston 17 sealingly slidable within a complementary bore 18.
  • the hydraulic fluid is contained within a closed hydraulic circuit 19 and throttled through a selectively adjustable control valve 20.
  • the torque transfer characteristics of the coupling for given differential velocities can thus be varied by adjustment of the control valve 20 by means of adjusting sleeve 21 on shaft 22.
  • the adjusting sleeve 21 includes spaced apart flanges which engage control valve actuating levers 23 connected with rotary control valve barrels 24 such that axial movement of the adjusting sleeve 21 effects a corresponding simultaneous rotation of the valve barrels 24 between the open and closed positions.
  • a complete lock-up condition between the input and output hubs can be achieved by closure of the control valves 24 as shown in the bottom half of figure 11. It will be apparent that the adjustment of the control valve to vary the torque-speed characteristic of the coupling right through to the lock-up condition can be effected by a suitable microprocessor or other electronic, hydraulic or mechanical control system whereby the coupling can be used adaptively to achieve a predetermined system response.
  • This form of the invention is particularly suitable for use in automotive applications to provide the desired torque bias characteristics in a limited slip differential, or to provide the required level of vibration absorption in a transmission coupling or controlled slip clutch.
  • a hydraulic slider assembly 50 includes an inner hub 51 and two outer hubs 52 and 53 disposed for relative coaxial rotational engagement.
  • the inner hub 51 includes a plurality of axially extending rectangular sliders 54. Sliders 54 are equally angularly spaced around the periphery of the hub 51 in complementary bores 55.
  • Outer hubs 52 and 53 are independently rotatable and axially opposed about hub 51 and include complementary sinuate tracks 56 and 57 respectively.
  • the tracks are continuous and slidably engage respective opposite axial ends of the sliders 54.
  • Sliders 54 are square in cross section and oscillate axially in the bores during relative movement of the inner and outer hubs.
  • the hydraulic fluid maintained between the hubs provides fluid resistance to the movement of the sliders and allows torque to be transferred between the hubs.
  • the inner hub 51 includes a plurality of axially extending fluid control slots (not shown) alternately spaced between the bores 55 to decrease the fluid resistance.
  • predetermined clearances are provided either between the sliders 54 and respective bores or the sliders 54 and the tracks 56 and 57 or both.
  • the differential carrier 30 is driven about an axis 32 by means of an input drive shaft 33.
  • the drive from input shaft 33 is subsequently diverted through 90° by a bevel pinion 34 in meshing engagement with a complementary bevel crown wheel 35 fixed with respect to the carrier 30.
  • the side gears 36 are respectively connected with a pair of coaxial mutually opposed outwardly depending half shafts 38 which in turn are connected to the driving wheels of the vehicle (not shown).
  • Figure 16 shows a first torque proportioning differential configuration wherein the hydraulic ball coupling 1 is effectively disposed intermediate the axle half-shafts 38.
  • the torque difference between the left and right hand shafts is approximately equal to twice the coupling torque and the angular velocity difference across the coupling corresponds to the wheel speed difference.
  • Figure 17 shows a second torque proportioning differential configuration wherein the coupling is positioned effectively between one of the axle shafts 38 and the differential carrier 30.
  • the torque difference between the left and right hand half-shafts corresponds to the coupling torque and the angular velocity difference across the coupling is equal to half the wheel speed difference.
  • the coupling is connected in the driveline in parallel with the differential.
  • the coupling can also be connected in series with the driveline as discussed later and used as a transmission element.
  • both wheels and hence both side gears rotate with approximately equal angular velocity and support approximately equal torque.
  • the resultant velocity difference across the fluid coupling in the differential gives rise to a resistance as the reciprocating sliders displace the fluid within their respective grooves while traversing the sinuate track.
  • the fluid resistance to movement of the sliders provides a locking torque which impedes differential rotation of the side gears and enables unequal torques to be transmitted to the driving wheels.
  • a principal advantage of the hydraulic slider coupling in a torque proportioning or limited slip differential is that the system is responsive to speed as opposed to the conventional torque responsive limited slip differentials.
  • the system provides low differential locking torque during cornering under normal driving conditions so as not to adversely affect vehicle handling and provides a gradual and progressive increase in resistive torque with increasing speed difference during conditions of wheel slip.
  • the hydraulic ball coupling partially absorbs transient shock loads applied to the driveline.
  • the shaft-to-shaft configuration produces approximately three times the locking torque of the "shaft-to-carrier” design for a given wheel speed difference. Consequently, the shaft-to-shaft design may be preferred in applications requiring high torques. On the other hand, in front wheel drive vehicular applications low torque bias may be preferred so as not to adversely affect vehicle handling, or cause excessive tyre wear and in this case the shaft-to-carrier design may be preferable.
  • the torque transfer characteristics of the coupling can be tailored to suit particular applications by the variation of a number of parameters including:-
  • the differential incorporating the hydraulic slider coupling according to the invention is also particularly effective in centre differential applications or as a torque transmission element in the drivelines of multiple wheel drive vehicles.
  • the hydraulic slider coupling of this invention provides a number of advantages.
  • the coupling is compact in relation to known viscous couplings and is readily adapted for incorporation into a differential to provide smooth and progressive speed responsive torque transfer under conditions of wheel spin.
  • the selectively variable torque transfer version incorporating the control valve provides a range of torque transmission characteristics up to full lock-up for a given speed difference, making the coupling particularly suitable for use in a differential to provide selective lock-up under adverse conditions of low traction to control wheel spin.
  • This form of the invention is equally applicable as a centre differential in multiple wheel drive vehicles.
  • the sliders and respective grooves share equally in the simultaneous generation of resistive torque so that the load on the individual sliders and the corresponding contact stresses on the track are relatively small as opposed to a system incorporating intermeshing gear teeth wherein only one to three teeth are in contact at any given time so that the resultant contact stresses are relatively high.
  • the invention is not limited to automotive applications but can be used to advantage in a variety of applications such as vibration absorbing elements, clutches, torque converters and the like.
  • the track could be disposed on the outer hub and the grooves on the inner hub.
  • the engaging surfaces of the hubs need not be cylindrical but could be conical, circular or annular or stepped for example.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Claims (15)

  1. Kupplung mit einer ersten Baugruppe (2; 51) und einer zweiten Baugruppe (3; 52, 53), die derart angeordnet sind, daß sie sich in zueinander drehbeweglichem Eingriff befinden, wobei eine dieser ersten (2) und zweiten (52, 53) Baugruppen eine sich über den Umfang erstreckende, kontinuierliche und im wesentlichen sich schlängelnde Bahn (4; 56, 57) umfaßt, die sich über mehrere Wellenlängen erstreckt, und die andere der ersten (51) und zweiten (3) Baugruppen eine Mehrzahl quer verlaufender Bahnen (6; 55) umfaßt, die sich im wesentlichen senkrecht zur Hauptrichtung der sich schlängelnden Bahn erstrecken; mit einer entsprechenden Mehrzahl von Gleitstücken (10; 54), die jeweils in sich überkreuzenden Bereichen der sich schlängelnden und der quer verlaufenden Bahnen angeordnet sind, so daß eine Relativ-Drehbewegung der ersten Baugruppe bezüglich der zweiten Baugruppe bewirkt, daß die Gleitstücke axial in den quer verlaufenden Bahnen oszillieren, während sie sich entlang der sich schlängelnden Bahn bewegen; und mit einem hydraulischen Fluid innerhalb der quer verlaufenden Bahnen, um den Oszillationen der Gleitstücke einen Widerstand entgegenzusetzen.
  2. Kupplung nach Anspruch 1, dadurch gekennzeichnet, daß die erste Baugruppe (2) eine innere Nabe ist, die die sich schlängelnde Bahn (4) auf einer äußeren, zylindrischen Oberfläche aufweist, und die zweite Baugruppe (3) eine entsprechende äußere Nabe ist, die die Mehrzahl der quer verlaufenden Bahnen (6) in Form von gleich beabstandeter, sich axial erstreckender Nuten oder Bohrungen in einer inneren zylindrischen Oberfläche der äußeren Nabe bildet, wobei die innere und äußere Nabe derart angeordnet sind, daß sie relativ zueinander koaxial rotieren können.
  3. Kupplung nach Anspruch 2, dadurch gekennzeichnet, daß die sich schlängelnden Bahn periodisch ausgebildet ist.
  4. Kupplung nach Anspruch 3, dadurch gekennzeichnet, daß die sich schlängelnde Bahn eine Sinusform aufweist.
  5. Kupplung nach Anspruch 1, dadurch gekennzeichnet, daß das Gleitstück (10) die Form einer Kugel und die sich schlängelnde (4) und die quer verlaufenden (6) Bahnen einen im wesentlichen halbkreisförmigen Querschnitt aufweisen.
  6. Kupplung nach Anspruch 1, dadurch gekennzeichnet, daß das Gleitstück die Form einer Kugel (11), die in ein zur oszillierenden Bewegung in der quer verlaufenden Bahn angeordnetes, prismatisches Gleitstück (10) eingreift, aufweist und daß die quer verlaufende Bahn durch eine komplementäre, prismatische Nut oder Bohrung gebildet ist.
  7. Kupplung nach Anspruch 6, dadurch gekennzeichnet, daß die quer verlaufende Bahn einen rechtwinkligen Querschnitt aufweist.
  8. Kupplung nach Anspruch 2, dadurch gekennzeichnet, daß zwischen der quer verlaufenden Bahn und dem Gleitstück ein Zwischenraum vorgesehen ist, durch welchen das hydraulische Fluid während der Oszillation des Gleitstücks hindurch gedrosselt wird.
  9. Kupplung nach Anspruch 2, dadurch gekennzeichnet, daß jedes Gleitstück einen abdichtend in einer entsprechenden quer verlaufenden Bahn verschiebbaren Kolben umfaßt.
  10. Kupplung nach Anspruch 9, dadurch gekennzeichnet, daß der Kolben eine Öffnung umfaßt, durch welche das hydraulische Fluid hindurch gedrosselt wird.
  11. Kupplung nach Anspruch 10, dadurch gekennzeichnet, daß das hydraulische Fluid in einer geschlossenen Schleife (19) geführt ist.
  12. Kupplung nach Anspruch 11, dadurch gekennzeichnet, daß das hydraulische Fluid durch ein wahlweise verstellbares Regelventil (20) in Abhängigkeit von der Oszillation des Kolbens gedrosselt ist.
  13. Kupplung nach Anspruch 1, dadurch gekennzeichnet, daß die erste Baugruppe eine innere Nabe (51) ist, die eine Mehrzahl von sich axial ersteckenden prismatischen Gleitstücken (54) umfaßt, wobei die Gleitstücke um die Peripherie der Nabe, in komplementären quer verlaufenden Bahnen (55) winkelbeabstandet angeordnet sind, und daß die zweite Baugruppe (52, 53) zwei axial voneinander beabstandete, äußere Naben umfaßt, die derart abgestützt sind, daß sie koaxial bezüglich der inneren Nabe rotieren können, und entgegengesetzt komplementäre sich schlängelnde Ausgestaltungen (56, 57) aufweisen und die sich schlängelnde Bahn für einen gleitenden Eingriff einander gegenüberliegender axialer Enden der Gleitstücke bilden und daß die innere Nabe derart angeordnet ist, daß sie sich im wesentlichen innerhalb der äußeren Naben relativ zu diesen drehen kann.
  14. Kupplung nach Anspruch 13, dadurch gekennzeichnet, daß die Gleitstücke einen im wesentlichen rechtwinkligen Querschnitt aufweisen und während der Relativbewegung der Naben in den quer verlaufenden Bahnen oszillieren.
  15. Kupplung nach Anspruch 14, dadurch gekennzeichnet, daß die innere Nabe eine Mehrzahl sich axial erstreckender Fluidsteuerungskanäle aufweist, die alternierend zwischen den quer verlaufenden Bahnen um die Peripherie der inneren Nabe beabstandet sind.
EP92910068A 1991-05-08 1992-05-07 Hydraulische gleitkupplung Expired - Lifetime EP0583336B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AUPK604091 1991-05-08
AU6040/91 1991-05-08
PCT/AU1992/000209 WO1992019881A1 (en) 1991-05-08 1992-05-07 Hydraulic slider coupling

Publications (3)

Publication Number Publication Date
EP0583336A1 EP0583336A1 (de) 1994-02-23
EP0583336A4 EP0583336A4 (en) 1994-06-29
EP0583336B1 true EP0583336B1 (de) 1997-03-12

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EP92910068A Expired - Lifetime EP0583336B1 (de) 1991-05-08 1992-05-07 Hydraulische gleitkupplung

Country Status (9)

Country Link
US (1) US5598911A (de)
EP (1) EP0583336B1 (de)
JP (1) JP3295700B2 (de)
KR (1) KR100292023B1 (de)
CN (1) CN1037368C (de)
CA (1) CA2102611C (de)
DE (1) DE69218191T2 (de)
PL (1) PL170057B1 (de)
WO (1) WO1992019881A1 (de)

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DE102009005838B4 (de) * 2009-01-21 2014-10-16 Gerhard Thien Getriebevorrichtung zum Übertragen eines Drehmoments und Vorrichtung zum Erzeugen oder Wandeln eines Drehmoments

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JP3295700B2 (ja) 2002-06-24
KR100292023B1 (ko) 2001-10-22
CA2102611A1 (en) 1992-11-09
EP0583336A4 (en) 1994-06-29
DE69218191T2 (de) 1997-10-09
JPH06507226A (ja) 1994-08-11
CN1070994A (zh) 1993-04-14
DE69218191D1 (de) 1997-04-17
US5598911A (en) 1997-02-04
PL170057B1 (pl) 1996-10-31
CA2102611C (en) 1997-10-21
CN1037368C (zh) 1998-02-11
WO1992019881A1 (en) 1992-11-12
EP0583336A1 (de) 1994-02-23

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